EP0654589A2 - Cylinder head lubricating system of an internal combustion engine - Google Patents
Cylinder head lubricating system of an internal combustion engine Download PDFInfo
- Publication number
- EP0654589A2 EP0654589A2 EP95101503A EP95101503A EP0654589A2 EP 0654589 A2 EP0654589 A2 EP 0654589A2 EP 95101503 A EP95101503 A EP 95101503A EP 95101503 A EP95101503 A EP 95101503A EP 0654589 A2 EP0654589 A2 EP 0654589A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- intake
- cylinder head
- camshaft
- exhaust
- lubricating system
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
- F01M9/10—Lubrication of valve gear or auxiliaries
- F01M9/102—Lubrication of valve gear or auxiliaries of camshaft bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/265—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder peculiar to machines or engines with three or more intake valves per cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/18—DOHC [Double overhead camshaft]
Definitions
- This invention relates to a cylinder head lubricating system of an internal combustion engine comprising a cylinder head, an intake and exhaust camshaft having cam lobes for operating a plurality of intake and exhaust valves, said intake and exhaust camshaft being supported in the cylinder head by intake and exhaust camshaft bearings, an oil pump, a first and a second lubricant conduit means extending to the intake and exhaust camshaft bearings respectively, wherein the length of the first lubricating conduit means from the oil pump to the intake camshaft bearings is shorter than the length of the second lubricating conduit means from the oil pump to the exhaust camshaft bearings.
- the normal arrangement for an engine having a camshaft and hydraulic lash adjusters is to supply lubricant through a common conduit from the lubricant pump to the lash adjusters and the cam journals.
- the engine may employ two camshafts, each of which operates its own series of valves through an actuating mechanism that includes its own series of lash adjusters.
- the pressure of the lubricant supplied to the lash adjusters will depend upon its distance from the lubricant pump and this means that the adjusters associated with one camshaft may receive lubricant at a substantially lower pressure than those associated with the other camshaft.
- the camshaft bearing structure tends to become complicated, as a plurality of cam lobes are necessary to actuate said intake and exhaust valves. Owing to the limited space available, it is often difficult to provide the necessary bearing surfaces on the camshaft or in the cylinder head. Frequently the engine employs a different number of intake valves and exhaust valves so that different external loads resulting from the valve actuating mechanisms act on the intake camshaft and the exhaust camshaft. Often known cylinder head lubricating systems do not meet said asymmetric requirements of the camshaft bearing structure.
- this objective is performed by a greater number of intake camshaft bearings than exhaust camshaft bearings, the intake camshaft being provided with a greater number of cam lobes than the exhaust camshaft for operating a greater number of intake valves than exhaust valves, wherein the camshaft bearings are disposed between the cam lobes operating the intake and exhaust valves of one cylinder of the engine.
- the different number of intake and exhaust camshaft bearings in connection with the respective length of the lubricating conduit means insures a substantial uniform lubricant pressure.
- the intake and/or exhaust camshaft bearings are integrally formed in part by the cylinder head provided with bosses defining bearing surfaces and in part by a cam cover provided with bosses defining bearing surfaces cooperating with the respective bearing surfaces of the cylinder head, wherein the first and second lubricating conduit means terminate in the cam cover bearing surfaces.
- the bosses for the intake camshaft are cut at their edges forming the boundary of the bearing surfaces. Accordingly, the width of the cam lobe and cam journal arrangement can be kept short in the direction of the camshaft axis.
- a multiple cylinder internal combustion engine constructed in accordance with an embodiment of the invention is identified generally by the reference numeral 21.
- the engine 21 includes a cylinder block which may be conventional and hence is only shown in phantom in Figure 3 in which a plurality of aligned bores 23 are formed.
- the engine 21 is of the four cylinder in line type. It should be readily apparent, however, to those skilled in the art how the invention can be practiced in conjunction with engines having other numbers of cylinders and other cylinder configurations.
- a cylinder head assembly indicated generally by the reference numeral 24 is affixed to the cylinder block 22 by means of a plurality of fasteners 25 that pass through appropriate openings in the cylinder head 24 and which are threaded into threaded openings in the cylinder block. It should be noted that the fasteners 25 are disposed so that they will be located at the four corners of the cylinder bores 23, as indicated by the broken circles in Figure 5, to show the relationship of these fasteners 25 to the cylinder bores 23.
- the lower face of the cylinder head 24 is provided with a plurality of recesses 26 which have a generally pent roof configuration, as will be described.
- Three intake valves comprised of a pair of side intake valves 27 and 28 and a center intake valve 29 are supported for reciprocation within the cylinder head 24 by respective valve guides 31. It will be noted that the intake valves 27, 28 and 29 are oriented so that the side intake valves 27 and 28 reciprocate along axes Y1 that are disposed at a relatively large acute angle ⁇ 2 to a plane A1 ( Figure 10) containing the cylinder bore axis X2 and extending parallel to the axis of rotation of the associated crankshaft.
- the center intake valve 29 reciprocates about an axis Y3 which is disposed at a lesser acute angle to this plane, this angle being indicated at ⁇ 1 in Figure 3.
- Each of the intake valves 27, 28 and 29 cooperates with a respective valve seat 32 pressed into the cylinder head 24 and defining an intake port at the termination of an intake passage 33 which extends through one side of the cylinder head.
- the intake passages 33 may be siamese so that one intake opening in the side of the cylinder head cooperates with each of the valve seats 32 or, alternatively, separate passages may be formed for each valve seat.
- the orientation of the heads of the valves 27, 28 and 29 gives the lower surface of the cylinder head cavity 26 a generally inclined portion 34 which extends across the plane A1 so that a portion of the heads of the valves 27 and 28 lies on the opposite side of this plane when the valves are closed, as clearly shown in Figure 10.
- Coil compression springs 34 encircle the stems of the valves 27, 28 and 29 and act against keeper retainer assemblies 35 for urging the valves 27, 28 and 29 to their closed positions.
- the mechanism for opening the intake valves 27, 28 and 29 will be described later.
- a pair of exhaust valves 36 and 37 are supported for reciprocation on the other side of the plane A1 by valve guides 38 which are pressed into the cylinder head assembly 24.
- the exhaust valves 36 and 37 reciprocate about respective axes Y2 which are disposed at an acute angle to the plane A1 which angle is less than the angle ⁇ 2 and greater than the angled ⁇ 1.
- the exhaust valves 36 and 37 cooperate with respective valve seats 39 that are pressed into the cylinder head 24 and which form the exhaust ports of exhaust passages 41 that extend through the side of the cylinder head 24 opposite to the intake side.
- the exhaust passages 41 may be separate or siamese. It should be noted that the disposition of the heads of the exhaust valves 36 and 37 gives rise to the combustion chamber cavity having a generally inclined surface 42 that intersects the surface 34 on the exhaust side of the plane A1 so that this intersection is slightly offset to the side of the combustion chamber.
- Coil compression springs 43 cooperate with keeper retainer assemblies 44 on the stems of the exhaust valves 36 and 37 for urging the exhaust valves 36 and 37 to their closed positions.
- the cylinder head 24 has an upstanding peripheral wall that defines an upwardly facing sealing surface 45 that defines in part a cavity 46 in which the valve actuating mechanism is contained.
- the cavity 46 is enclosed by means of a cam cover 47 that is affixed to the cylinder head 24 in a manner as will be described.
- On the intake side of the cylinder head 24 there is provided a plurality of bosses 48 which define generally semi cylindrical shaped bearing surfaces 49. Adjacent the bosses 48, there are provided further bosses 51 that define quarter cylindrical bearing surfaces 52.
- An intake camshaft indicated generally by the reference numeral 53 has spaced bearing surfaces 54 that are received within and journaled on the cylinder head bearing surfaces 49 and 52.
- the cylinder head 24 further has end bosses 55 that define further semi cylindrical bearing surfaces with which bearing portions 56 of the camshaft 53 cooperate so as to rotatably journal it.
- the cam cover 47 has a plurality of inwardly extending portions 58 that define semi cylindrical bearing surfaces 59 which cooperate with the camshaft bearing surfaces 54 and 56, respectively, so as to complete the journaling of the intake camshaft 53 in the cylinder head assembly.
- bosses 51 and 48 formed in the cylinder head 24 and the bosses 58 formed in the cam cover 47 are cut at their edges forming the boundary of the bearing surfaces 49, 52 and 59.
- the exhaust side of the cylinder head assembly 24 also has a plurality of inwardly extending bosses 61 which have respective bearing surfaces 62 which are of a semi cylindrical configuration.
- An exhaust camshaft 63 is rotatably journaled on these bearing surfaces by means of bearing portions 64 formed integrally thereon.
- end walls 65 of the cylinder head 24 are provided with bearing surfaces 66 which cooperate with end bearing surfaces 67 on the exhaust camshaft 63 for its rotational support. It should be noted that the intake camshaft 53 and exhaust camshaft 63 rotate about parallel axes which are parallel to the axis of rotation of the associated crankshaft.
- bearing surfaces 68 Cooperating with the cylinder head bearing surfaces 62 and 66 are bearing surfaces 68 formed in inwardly extending portions 69 of the cam cover 47.
- the cam cover 47 is provided with a plurality of appropriately spaced bolt clearance holes 71 that are positioned in a pattern as best shown in Figure 6, and which receive bolts 72 that are threaded into tapped openings formed in the cylinder head 24 so as to secure the bearing caps formed by the cam cover 47 and the cam cover in place. Because of this construction, the head assembly may be made more compact than prior art arrangements and also the use of separate bearing caps for the camshaft may be avoided.
- a toothed sprocket 73 ( Figure 5) is affixed to one exposed end of the exhaust camshaft 63 and is driven by a toothed belt 74 in timed relationship with the engine crankshaft (not shown).
- a sprocket 75 At the opposite end of the exhaust camshaft 63, and within the cylinder head assembly 24, there is affixed a sprocket 75.
- a chain 76 encircles the sprocket 75 and drives a sprocket 77 that is affixed to the intake camshaft 53 at this end. In this way, the intake and exhaust camshafts will be driven in timed relationship from the engine output shaft.
- cam lobes 78 On the intake camshaft 53 for each cylinder.
- One of the cam lobes 78 is disposed between the bearing surfaces 49 and 52 and the camshaft bearing surfaces 54.
- the other of the cam lobes 78 are positioned outwardly of these bearing surfaces.
- Individual rocker arm assemblies 79 ( Figures 2 and 3) have an intermediate portion that is engaged by the cam lobe 78 and an end portion that is engaged with the stem of the respective intake valve 27, 28 and 29.
- the rocker arms 79 are pivotally supported by means of a hydraulically operated lash adjuster, indicated generally by the reference numeral 81 and having a construction as best shown in Figure 2.
- Each lash adjuster 81 comprises a cylindrical body portion 82 having an internal bore in which a tappet member 83 is slidably supported.
- the tappet member 83 has a hollow central portion 84 which communicates with a pressure chamber 85 positioned at the bottom of the adjuster body 82 through a passageway 86 in which a spring biased check valve 87 is positioned.
- Hydraulic pressure is delivered to the central interior 84 of the adjusting member from a delivery passage 88 formed in the body 82 and a delivery passage 89 formed in the tappet 83.
- the hydraulic pressure acts under the tappet 83 so as to hold the clearance in the system to zero clearance.
- a light compression spring 91 also acts to hold the tappet 83 in position when the engine is not running.
- a further passage 92 extends through the tappet 83 and communicates with a spherical socket 93 formed in the rocker arm 79 for lubrication.
- a delivery passage supplies oil to the lash adjuster 81 for the aforedescribed operation.
- the bores in which the adjusters 81 are positioned are indicated by the reference numeral 94 and are oriented as described in my aforenoted copending application. These bores terminate in lower shoulders 95 against which the adjuster bodies 82 react.
- the exhaust camshaft 63 is provided with pairs of cam lobes 96 that are disposed on opposite sides of their bearing portions 64 so as to operate the exhaust valves 36 and 37. These cam lobes 96 cooperate with intermediate portions of exhaust rocker arms 97 which have one end portion engaged with the stems of the valves 36 and 37 for operating them. The opposite ends of the rocker arms 97 cooperate with hydraulic lash adjusters 98 which have an internal construction the same as those associated with the intake valves (lash adjusters 81). For this reason, the description of the exhaust lash adjusters 98 is not believed to be necessary.
- adjusters 98 are received in bores 99 configured as described in my aforenoted copending application and which have their tappets 83 cooperating with spherical recesses 101 in the rocker arms 97.
- the base of the bores 99 is formed with a surface 102 against which the adjuster body reacts.
- the engine 21 is provided with a lubricating system that includes an oil reservoir which may be of either the wet or dry sump type and at least a pressure pump, indicated generally by the reference numeral 103 in Figures 1 and 7.
- the pump 103 is driven from the engine output shaft in a suitable manner and lubricates the crankshaft and components associated with the cylinder block in a well known manner.
- this lubrication system includes a passageway that extends through the cylinder block 22 and which cooperates with a main oil delivery passage 104 ( Figure 1) that extends upwardly through the lower face of the cylinder head 24 between a pair of cylinders thereof.
- the passageway 104 is, in the illustrated embodiment, on the intake side of the cylinder head 24 for a reason to be described.
- a cross drilled passageway 105 intersects the passage 104 and is closed by a closure plug 106.
- a further drilled passageway 107 extends down from the cylinder head sealing surface 45 through a side wall 108 of the cylinder head and intersects the passageway 105.
- a sleeve 109 is pressed into this passageway and cooperates with a corresponding passageway 111 formed in a side wall 112 of the cam cover 47.
- a cross drilled passageway 113 extends transversely across the cam cover 47 as shown in Figures 1 and 6, and intersects the passageway 111.
- This cross drilled passageway 113 is closed at its outer end by means of a closure plug 114.
- a further passageway 115 is drilled in the opposite wall 116 of the cam cover 47 and cooperates with a sleeve 117 that is pressed into a side wall 118 of the cylinder head 24 around a further oil passageway 119 which is likewise drilled in the cylinder head 24.
- the passageway 105 at the intake side of the cylinder head assembly is intersected by a transversely extending oil gallery 121 which intersects the bores 94 in which the lash adjusters 81 are slidably supported adjacent the delivery ports 88.
- a series flow oil delivery for supplying lubricant under pressure to the intake adjusters 81.
- a gallery 122 is drilled in the opposite wall 118 of the cylinder head and intersects the bores 99 in which the exhaust valve adjusters 98 are positioned. Since the intake oil gallery 121 is closer to the source of oil pressure, there is a greater likelihood that uniform pressure will be delivered to both the intake adjusters 81 and exhaust adjusters 98, bearing in mind the fact that there are more intake adjusters than exhaust adjusters, and thus the system will operate at a more uniform pressure.
- one or more oil drain passageways 128 are formed in the cylinder head 24 for draining lubricant back to the crankcase of the engine.
- Each combustion chamber of the engine is provided with a single spark plug for firing the charge therein.
- the cylinder head 24 is provided with a tapped opening 129 for receiving the spark plug. This tapped opening is formed at the base of the larger opening 131.
- the cam cover has an even larger opening 132 for accessing these spark plugs. This construction appears best in Figure 9.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
Description
- This invention relates to a cylinder head lubricating system of an internal combustion engine comprising a cylinder head, an intake and exhaust camshaft having cam lobes for operating a plurality of intake and exhaust valves, said intake and exhaust camshaft being supported in the cylinder head by intake and exhaust camshaft bearings, an oil pump, a first and a second lubricant conduit means extending to the intake and exhaust camshaft bearings respectively, wherein the length of the first lubricating conduit means from the oil pump to the intake camshaft bearings is shorter than the length of the second lubricating conduit means from the oil pump to the exhaust camshaft bearings.
- The use of overhead valves operated by overhead mounted camshafts is well known. Although there are some advantages to direct valve actuation, the use of a rocker arm actuator has the advantage of permitting the incorporation of a hydraulic lash adjuster. Conventionally it has been the practice to supply lubricant to the lash adjusters for their operation and to the journals of the associated camshaft in a series flow relationship. Although this has the advantage of simplicity, it has certain disadvantages. Specifically, with a series flow arrangement when the engine is turned off, the fact that the camshaft journals are open to the atmosphere will cause leak down of the lubricant. That is, because the cam journals are generally open, the system does not maintain pressure and lubricant can drain down back through the series flow arrangement into the lubricant reservoir through the oil pump. This means that the lubricant in the lifters will become depleted when the engine is shut down. This can give rise to obvious difficulties on restarting.
- As has been noted, the normal arrangement for an engine having a camshaft and hydraulic lash adjusters is to supply lubricant through a common conduit from the lubricant pump to the lash adjusters and the cam journals. Frequently the engine may employ two camshafts, each of which operates its own series of valves through an actuating mechanism that includes its own series of lash adjusters. With the type flow arrangement previously proposed, the pressure of the lubricant supplied to the lash adjusters will depend upon its distance from the lubricant pump and this means that the adjusters associated with one camshaft may receive lubricant at a substantially lower pressure than those associated with the other camshaft.
- From EP-A-0 212 981 an oil supply system for a valve operating mechanism in internal combustion engines is known. In that case the number of lash adjustors at the intake and exhaust sides is the same and difficulties in view of a uniform distribution of the lubricating oil pressure are not indicated.
- From US-A-4 709 667 a cylinder head lubricating system is known, wherein the conduits extending to the intake lash adjusters and the exhaust lash adjusters have a different length from the oil pump. The number of lash adjusters on the intake and exhaust side is the same and similar difficulties arise in distributing a uniform oil pressure. Moreover, the main oil conduit provides too little space causing a high flow resistance for supplying much lubricant.
- In an arrangement incorporating a system for precluding leak down of the hydraulic lifters, a still further problem can result, particularly where the arrangement utilizes two camshafts and a plurality of lifters associated with it. Frequently, the arrangement is such that each cylinder of the engine is provided with different numbers of intake and exhaust valves. Where this is the case, a greater number of hydraulic lash adjusters may be associated with one camshaft than the other. This further aggravates the problems already discussed.
- In connection with valve arrangements of the type already described, it is generally necessary to deliver oil to the camshafts through the cylinder block and cylinder head. The camshafts are conventionally journaled on the cylinder head by bearing surfaces formed integrally with the cylinder head and separate bearing caps that are affixed to the cylinder head. With such an arrangement, it is generally the practice to deliver the oil to one end of the camshaft by means of a passage that is formed in the cylinder head and this obviously adds to the length of the engine. Also, the internal passages of the cylinder head may, itself, present certain problems in connection with maintaining a compact construction.
- When an engine has a plurality of intake and exhaust valves per cylinder, the camshaft bearing structure tends to become complicated, as a plurality of cam lobes are necessary to actuate said intake and exhaust valves. Owing to the limited space available, it is often difficult to provide the necessary bearing surfaces on the camshaft or in the cylinder head. Frequently the engine employs a different number of intake valves and exhaust valves so that different external loads resulting from the valve actuating mechanisms act on the intake camshaft and the exhaust camshaft. Often known cylinder head lubricating systems do not meet said asymmetric requirements of the camshaft bearing structure.
- Accordingly, it is an objective of the present invention to provide an improved cylinder head lubricating system of an internal combustion engine with a simple structure for supplying the camshaft bearing structure with a substantially uniform lubricant pressure.
- According to the present invention, this objective is performed by a greater number of intake camshaft bearings than exhaust camshaft bearings, the intake camshaft being provided with a greater number of cam lobes than the exhaust camshaft for operating a greater number of intake valves than exhaust valves, wherein the camshaft bearings are disposed between the cam lobes operating the intake and exhaust valves of one cylinder of the engine.
- The different number of intake and exhaust camshaft bearings in connection with the respective length of the lubricating conduit means insures a substantial uniform lubricant pressure.
- According to a preferred embodiment of the present invention, the intake and/or exhaust camshaft bearings are integrally formed in part by the cylinder head provided with bosses defining bearing surfaces and in part by a cam cover provided with bosses defining bearing surfaces cooperating with the respective bearing surfaces of the cylinder head, wherein the first and second lubricating conduit means terminate in the cam cover bearing surfaces.
- In a preferred embodiment, the bosses for the intake camshaft are cut at their edges forming the boundary of the bearing surfaces. Accordingly, the width of the cam lobe and cam journal arrangement can be kept short in the direction of the camshaft axis.
- Further preferred embodiments of the invention are laid down in further dependent claims.
- Hereinafter, the present invention is illustrated and explained in greater detail by means of preferred embodiments in connection with accompanying drawings, wherein:
- Figure 1 is a transverse cross sectional view taken through a cylinder head assembly constructed in accordance with an embodiment of the invention and is taken generally along the line 1-1 of Figure 5,
- Figure 2 is an enlarged cross sectional view of one of the hydraulic lash adjusters,
- Figure 3 is a partial cross sectional view taken generally along the line 3-3 of Figure 5, showing the cylinder block and cam cover in phantom,
- Figure 4 is a cross sectional view taken along the line 4-4 of Figure 5, with a portion of the cylinder head assembly shown in phantom,
- Figure 5 is a top plan view of the cylinder head assembly with the cam cover removed and portions of the camshafts broken away,
- Figure 6 is a top plan view of the cam cover,
- Figure 7 is a schematic view showing how the lubricant system is related to the cam bearing journals and the hydraulic lash adjusters,
- Figure 8 is a cross sectional view taken along the line 8-8 of Figure 4,
- Figure 9 is a cross sectional view taken along the line 9-9 of Figure 6,
- Figure 10 is a bottom plan view of the combustion chamber.
- Referring now in detail to the drawings and initially primarily to Figure 1, a multiple cylinder internal combustion engine, constructed in accordance with an embodiment of the invention is identified generally by the
reference numeral 21. Theengine 21 includes a cylinder block which may be conventional and hence is only shown in phantom in Figure 3 in which a plurality of alignedbores 23 are formed. In the illustrated embodiment, theengine 21 is of the four cylinder in line type. It should be readily apparent, however, to those skilled in the art how the invention can be practiced in conjunction with engines having other numbers of cylinders and other cylinder configurations. - Since the invention deals primarily with the cylinder head assembly and more particularly to the valve actuating mechanism therefor, the details of the cylinder block, pistons and running component of the engine which may be considered to be conventional are not believed to be necessary to enable those skilled in art to practice the invention. Therefore, the cylinder head and valve train assembly and lubrication system therefor will now be described by particular reference to Figures 1, 4, 5 and 10 in addition to Figure 3.
- A cylinder head assembly, indicated generally by the
reference numeral 24 is affixed to thecylinder block 22 by means of a plurality offasteners 25 that pass through appropriate openings in thecylinder head 24 and which are threaded into threaded openings in the cylinder block. It should be noted that thefasteners 25 are disposed so that they will be located at the four corners of thecylinder bores 23, as indicated by the broken circles in Figure 5, to show the relationship of thesefasteners 25 to thecylinder bores 23. - The lower face of the
cylinder head 24 is provided with a plurality ofrecesses 26 which have a generally pent roof configuration, as will be described. Three intake valves comprised of a pair ofside intake valves center intake valve 29 are supported for reciprocation within thecylinder head 24 byrespective valve guides 31. It will be noted that theintake valves side intake valves - The
center intake valve 29 reciprocates about an axis Y₃ which is disposed at a lesser acute angle to this plane, this angle being indicated at α₁ in Figure 3. - Each of the
intake valves respective valve seat 32 pressed into thecylinder head 24 and defining an intake port at the termination of anintake passage 33 which extends through one side of the cylinder head. Theintake passages 33 may be siamese so that one intake opening in the side of the cylinder head cooperates with each of thevalve seats 32 or, alternatively, separate passages may be formed for each valve seat. The orientation of the heads of thevalves inclined portion 34 which extends across the plane A₁ so that a portion of the heads of thevalves - Coil compression springs 34 encircle the stems of the
valves keeper retainer assemblies 35 for urging thevalves intake valves - A pair of
exhaust valves valve guides 38 which are pressed into thecylinder head assembly 24. Theexhaust valves exhaust valves respective valve seats 39 that are pressed into thecylinder head 24 and which form the exhaust ports ofexhaust passages 41 that extend through the side of thecylinder head 24 opposite to the intake side. As with theintake passages 33, theexhaust passages 41 may be separate or siamese. It should be noted that the disposition of the heads of theexhaust valves inclined surface 42 that intersects thesurface 34 on the exhaust side of the plane A₁ so that this intersection is slightly offset to the side of the combustion chamber. - Coil compression springs 43 cooperate with
keeper retainer assemblies 44 on the stems of theexhaust valves exhaust valves - The mechanism for opening the
intake valves exhaust valves respective springs cylinder head 24 has an upstanding peripheral wall that defines an upwardly facing sealingsurface 45 that defines in part acavity 46 in which the valve actuating mechanism is contained. Thecavity 46 is enclosed by means of acam cover 47 that is affixed to thecylinder head 24 in a manner as will be described. On the intake side of thecylinder head 24 there is provided a plurality ofbosses 48 which define generally semi cylindrical shaped bearing surfaces 49. Adjacent thebosses 48, there are providedfurther bosses 51 that define quarter cylindrical bearing surfaces 52. An intake camshaft, indicated generally by thereference numeral 53 has spaced bearing surfaces 54 that are received within and journaled on the cylinder head bearing surfaces 49 and 52. Thecylinder head 24 further hasend bosses 55 that define further semi cylindrical bearing surfaces with which bearingportions 56 of thecamshaft 53 cooperate so as to rotatably journal it. Unlike conventional arrangements wherein separate bearing caps are provided, in accordance with a feature of the invention, thecam cover 47 has a plurality of inwardly extendingportions 58 that define semi cylindrical bearing surfaces 59 which cooperate with the camshaft bearing surfaces 54 and 56, respectively, so as to complete the journaling of theintake camshaft 53 in the cylinder head assembly. - As can be best seen from figure 8, the
bosses cylinder head 24 and thebosses 58 formed in thecam cover 47 are cut at their edges forming the boundary of the bearing surfaces 49, 52 and 59. - The exhaust side of the
cylinder head assembly 24 also has a plurality of inwardly extendingbosses 61 which have respective bearing surfaces 62 which are of a semi cylindrical configuration. Anexhaust camshaft 63 is rotatably journaled on these bearing surfaces by means of bearingportions 64 formed integrally thereon. In addition,end walls 65 of thecylinder head 24 are provided with bearingsurfaces 66 which cooperate with end bearing surfaces 67 on theexhaust camshaft 63 for its rotational support. It should be noted that theintake camshaft 53 andexhaust camshaft 63 rotate about parallel axes which are parallel to the axis of rotation of the associated crankshaft. - Cooperating with the cylinder head bearing surfaces 62 and 66 are bearing
surfaces 68 formed in inwardly extendingportions 69 of thecam cover 47. - The
cam cover 47 is provided with a plurality of appropriately spacedbolt clearance holes 71 that are positioned in a pattern as best shown in Figure 6, and which receivebolts 72 that are threaded into tapped openings formed in thecylinder head 24 so as to secure the bearing caps formed by thecam cover 47 and the cam cover in place. Because of this construction, the head assembly may be made more compact than prior art arrangements and also the use of separate bearing caps for the camshaft may be avoided. - A toothed sprocket 73 (Figure 5) is affixed to one exposed end of the
exhaust camshaft 63 and is driven by atoothed belt 74 in timed relationship with the engine crankshaft (not shown). At the opposite end of theexhaust camshaft 63, and within thecylinder head assembly 24, there is affixed a sprocket 75. Achain 76 encircles the sprocket 75 and drives asprocket 77 that is affixed to theintake camshaft 53 at this end. In this way, the intake and exhaust camshafts will be driven in timed relationship from the engine output shaft. - In order to operate the
intake valves cam lobes 78 on theintake camshaft 53 for each cylinder. One of thecam lobes 78 is disposed between the bearing surfaces 49 and 52 and the camshaft bearing surfaces 54. The other of thecam lobes 78 are positioned outwardly of these bearing surfaces. Individual rocker arm assemblies 79 (Figures 2 and 3) have an intermediate portion that is engaged by thecam lobe 78 and an end portion that is engaged with the stem of therespective intake valve rocker arms 79 are pivotally supported by means of a hydraulically operated lash adjuster, indicated generally by thereference numeral 81 and having a construction as best shown in Figure 2. - Each lash
adjuster 81 comprises acylindrical body portion 82 having an internal bore in which atappet member 83 is slidably supported. Thetappet member 83 has a hollowcentral portion 84 which communicates with apressure chamber 85 positioned at the bottom of theadjuster body 82 through apassageway 86 in which a springbiased check valve 87 is positioned. Hydraulic pressure is delivered to thecentral interior 84 of the adjusting member from adelivery passage 88 formed in thebody 82 and adelivery passage 89 formed in thetappet 83. The hydraulic pressure acts under thetappet 83 so as to hold the clearance in the system to zero clearance. Alight compression spring 91 also acts to hold thetappet 83 in position when the engine is not running. - A
further passage 92 extends through thetappet 83 and communicates with aspherical socket 93 formed in therocker arm 79 for lubrication. A delivery passage, to be described, supplies oil to thelash adjuster 81 for the aforedescribed operation. - The bores in which the
adjusters 81 are positioned are indicated by thereference numeral 94 and are oriented as described in my aforenoted copending application. These bores terminate inlower shoulders 95 against which theadjuster bodies 82 react. - The
exhaust camshaft 63 is provided with pairs ofcam lobes 96 that are disposed on opposite sides of theirbearing portions 64 so as to operate theexhaust valves cam lobes 96 cooperate with intermediate portions ofexhaust rocker arms 97 which have one end portion engaged with the stems of thevalves rocker arms 97 cooperate with hydraulic lashadjusters 98 which have an internal construction the same as those associated with the intake valves (lash adjusters 81). For this reason, the description of the exhaust lashadjusters 98 is not believed to be necessary. - However, these
adjusters 98 are received inbores 99 configured as described in my aforenoted copending application and which have theirtappets 83 cooperating with spherical recesses 101 in therocker arms 97. The base of thebores 99 is formed with asurface 102 against which the adjuster body reacts. - The
engine 21 is provided with a lubricating system that includes an oil reservoir which may be of either the wet or dry sump type and at least a pressure pump, indicated generally by thereference numeral 103 in Figures 1 and 7. Thepump 103 is driven from the engine output shaft in a suitable manner and lubricates the crankshaft and components associated with the cylinder block in a well known manner. In accordance with the invention, this lubrication system includes a passageway that extends through thecylinder block 22 and which cooperates with a main oil delivery passage 104 (Figure 1) that extends upwardly through the lower face of thecylinder head 24 between a pair of cylinders thereof. Thepassageway 104 is, in the illustrated embodiment, on the intake side of thecylinder head 24 for a reason to be described. A cross drilledpassageway 105 intersects thepassage 104 and is closed by aclosure plug 106. A further drilledpassageway 107 extends down from the cylinderhead sealing surface 45 through aside wall 108 of the cylinder head and intersects thepassageway 105. Asleeve 109 is pressed into this passageway and cooperates with acorresponding passageway 111 formed in aside wall 112 of thecam cover 47. - A cross drilled
passageway 113 extends transversely across thecam cover 47 as shown in Figures 1 and 6, and intersects thepassageway 111. This cross drilledpassageway 113 is closed at its outer end by means of aclosure plug 114. - A
further passageway 115 is drilled in theopposite wall 116 of thecam cover 47 and cooperates with asleeve 117 that is pressed into aside wall 118 of thecylinder head 24 around afurther oil passageway 119 which is likewise drilled in thecylinder head 24. - The
passageway 105 at the intake side of the cylinder head assembly is intersected by a transversely extendingoil gallery 121 which intersects thebores 94 in which thelash adjusters 81 are slidably supported adjacent thedelivery ports 88. Hence, there is defined a series flow oil delivery for supplying lubricant under pressure to theintake adjusters 81. - In a similar manner, a
gallery 122 is drilled in theopposite wall 118 of the cylinder head and intersects thebores 99 in which theexhaust valve adjusters 98 are positioned. Since theintake oil gallery 121 is closer to the source of oil pressure, there is a greater likelihood that uniform pressure will be delivered to both theintake adjusters 81 andexhaust adjusters 98, bearing in mind the fact that there are more intake adjusters than exhaust adjusters, and thus the system will operate at a more uniform pressure. Also, because of the fact that theadjuster galleries passageways adjusters - This concept may be best understood by reference to Figure 7 where the main oil gallery aforereferred to is identified by the
reference numeral 123. As may be seen in this Figure, intakecamshaft delivery passages 124 intersect thismain gallery 123 and exhaustcamshaft delivery passages 125 also intersect this gallery. As may be seen in Figures 1, 4, 6, 7 and 8, these passages extend through thebosses cam cover 47 for lubricating these journals. Thepassageways 124 are all supplied with lubricant from a cross drilledpassageway 126 that extends along thecam cover 47 and which is closed at one end thereof by means of a plug (not shown). In a like manner, a drilledpassageway 127 that extends parallel to thepassageway 126 intersects thepassageways 125 and supplies lubricant to them for theexhaust camshaft journals 64. - It should be readily apparent that the described construction insures that there will be adequate lubrication for the camshaft journals and also adequate lubrication supplied to the hydraulic lash
adjusters cam cover 47, the overall engine construction may be made more compact. Furthermore, since the delivery to thegallery 121 for the more numerous intake lashadjusters 81 is closer to it than that for theexhaust gallery 122, there will not be a substantial pressure difference between the intake and exhaust adjusters. - As may be seen in Figure 1, one or more
oil drain passageways 128 are formed in thecylinder head 24 for draining lubricant back to the crankcase of the engine. - Each combustion chamber of the engine is provided with a single spark plug for firing the charge therein. The
cylinder head 24 is provided with a tappedopening 129 for receiving the spark plug. This tapped opening is formed at the base of thelarger opening 131. The cam cover has an evenlarger opening 132 for accessing these spark plugs. This construction appears best in Figure 9.
Claims (15)
- Cylinder head lubricating system of an internal combustion engine (21) comprising a cylinder head (24), an intake and exhaust camshaft (53; 63) having cam lobes (78, 96) for operating a plurality of intake and exhaust valves (27, 28, 29; 36, 37), said intake and exhaust camshaft (53; 63) being supported in the cylinder head (24) by intake and exhaust camshaft bearings (49, 52, 59; 62, 68), an oil pump (103), a first and a second lubricant conduit means (104, 105, 107, 124; 104, 105, 107, 124) extending to the intake and exhaust camshaft bearings (49, 52, 59; 62, 68) respectively, wherein the length of the first lubricating conduit means (104, 105, 107, 124) from the oil pump (103) to the intake camshaft bearings (49, 52, 59) is shorter than the length of the second lubricating conduit means (104, 105, 107, 124) from the oil pump (103) to the exhaust camshaft bearings (62, 68), characterised by a greater number of intake camshaft bearings (49, 52, 59) than exhaust camshaft bearings (62, 68), the intake camshaft (53) being provided with a greater number of cam lobes (78) than the exhaust camshaft (63) for operating a greater number of intake valves (27, 28, 29) than exhaust valves (36, 37) wherein the camshaft bearings (49, 52, 59; 62, 68) are disposed between the cam lobes (78, 96) operating the intake and exhaust valves (27, 28, 29; 36, 37) of one cylinder of the engine (21).
- Cylinder head lubricating system as claimed in claim 1, characterised in that two intake camshaft bearings (49, 52, 59) are disposed between two outer cam lobes (78) for operating a pair of side intake valves (27, 28), a central cam lobe (78) of the intake camshaft (53) for operating a central intake valve (29) being disposed between said two intake camshaft bearings (49, 52, 59) and an exhaust camshaft bearing (62, 68) is disposed between two cam lobes (96) of the exhaust camshaft (63) for operating two exhaust valves (36, 37), wherein the width of said two intake camshaft bearings (49, 52, 59) is smaller than the width of said exhaust camshaft bearing (62, 64).
- Cylinder head lubricating system as claimed in claim 1 or 2, characterised in that the intake and/or exhaust camshaft bearings are integrally formed in part by the cylinder head (24) provided with bosses (48, 51, 61) defining bearing surfaces (49, 52, 62) and in part by a cam cover (47) provided with bosses (58, 69) defining bearing surfaces (59, 68) cooperating with the respective bearing surfaces (49, 52, 62) of the cylinder head (24), wherein the first and second lubricating conduit means (104, 105, 107, 124; 104, 105, 107, 124) terminate in the cam cover bearing surfaces (59, 62).
- Cylinder head lubricating system as claimed in claim 3, characterised in that the bosses (48, 51, 58) for the intake camshaft (53) are cut at their edges forming the boundary of the bearing surfaces (49, 52, 59).
- Cylinder head lubricating system as claimed in claim 3 or 4, characterised in that a pair of bosses (48, 51) are provided for the intake camshaft (53) per cylinder, a first one of said bosses (48) defining a semi-cylindrically shaped bearing surface (49) and a second one of said bosses (51) defining a quarter-cylindrically shaped bearing surface (52).
- Cylinder head lubricating system as claimed in at least one of claims 1 to 5, characterised in that the first and second lubricant conduit means (104, 105, 107, 124; 104, 105, 107, 113, 124) are formed at least in part in the cylinder head (24) and in the cam cover (47).
- Cylinder head lubricating system as claimed in at least one of claims 1 to 6, characterised in that the first and second lubricant conduit means (104, 105, 107, 124; 104, 105, 107, 125) are communicated with each other via a third lubricant conduit means (113).
- Cylinder head lubricating system as claimed in claim 7, characterised in that the first, second and third lubricant conduit means are bores (104, 105, 107, 113, 124, 125) formed in the cylinder head (24) and the cam cover (47), respectively.
- Cylinder head lubricating system as claimed in at least one of claims 1 to 8, characterised in that a main oil delivery passage (104) which forms part of the first lubricant conduit means (104, 105, 107, 124) extends upwardly outside of head bolt bores through a lower portion of the cylinder head (24).
- Cylinder head lubricating system as claimed in at least one of claims 1 to 9, characterised by a first series of hydraulic lash adjusters (81) for operating the intake valves (27, 28, 29) and a second series of hydraulic lash adjusters (98) for operating the exhaust valves (36, 37), said lash adjusters (81, 98) being communicated with the first and second lubricant conduit means (104, 105, 107, 124; 104, 105, 107, 113, 125) via a fourth lubricant conduit means (121, 122).
- Cylinder head lubricating system as claimed in claim 10, characterised by three intake lash adjusters (81) for operating three intake valves (27, 28, 29) and two exhaust lash adjusters (98) for operating two exhaust valves (36, 37).
- Cylinder head lubricating system as claimed in claim 10 or 11, characterised in that the intake and exhaust cam shaft bearings (49, 52, 59; 62, 68) and the lash adjusters (81, 98) are lubricated in series.
- Cylinder head lubricating system as claimed in at least one of claims 10 to 12, characterised by lubricant being supplied to the camshaft bearings (49, 52, 59; 62, 68) in a series flow relationship with the lubricant being supplied to the lash adjusters (81, 98) associated with each of the camshafts (53, 63) in a parallel flow relationship and with the individual lash adjusters (81, 98) associated with each camshaft (53, 63) being lubricated in a series flow relationship.
- Cylinder head lubricating system as claimed in at least one of claims 10 to 13, characterised in that the lubricant is delivered to the lubricant system adjacent the intake camshaft (53) having the greater number of lash adjusters (81) for maintaining substantially the same lubricant pressure to all lash adjusters (81, 98).
- Cylinder head lubricating system as claimed in at least one of claims 10 to 14, characterised in that a plurality of cylinders are associated with the cylinder head (24) in line.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP181893/89 | 1989-07-14 | ||
JP1181893A JP2829866B2 (en) | 1989-07-14 | 1989-07-14 | Lubrication system for 4-cycle engine |
EP19900113491 EP0408081B1 (en) | 1989-07-14 | 1990-07-13 | Cylinder head lubricating system of an internal combustion engine |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900113491 Division-Into EP0408081B1 (en) | 1989-07-14 | 1990-07-13 | Cylinder head lubricating system of an internal combustion engine |
EP90113491.6 Division | 1990-07-13 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0654589A2 true EP0654589A2 (en) | 1995-05-24 |
EP0654589A3 EP0654589A3 (en) | 1995-06-28 |
EP0654589B1 EP0654589B1 (en) | 1997-12-10 |
Family
ID=16108730
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900113491 Expired - Lifetime EP0408081B1 (en) | 1989-07-14 | 1990-07-13 | Cylinder head lubricating system of an internal combustion engine |
EP95101503A Expired - Lifetime EP0654589B1 (en) | 1989-07-14 | 1990-07-13 | Cylinder head lubricating system of an internal combustion engine |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900113491 Expired - Lifetime EP0408081B1 (en) | 1989-07-14 | 1990-07-13 | Cylinder head lubricating system of an internal combustion engine |
Country Status (3)
Country | Link |
---|---|
EP (2) | EP0408081B1 (en) |
JP (1) | JP2829866B2 (en) |
DE (2) | DE69024117T2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0854272A1 (en) * | 1997-01-21 | 1998-07-22 | Isuzu Motors Limited | A valve operating apparatus of DOHC |
EP0890713A3 (en) * | 1997-07-12 | 1999-03-31 | DEUTZ Aktiengesellschaft | Camshaft bearing frame |
EP1006272A3 (en) * | 1998-12-01 | 2003-01-29 | Honda Giken Kogyo Kabushiki Kaisha | Cylinder head structure in multi-cylinder engine |
CN109707526A (en) * | 2018-12-26 | 2019-05-03 | 郭严成 | A kind of automobile engine using new energy resources cylinder cap of positioning igniting |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE69414557T2 (en) * | 1994-06-15 | 1999-04-01 | Yamaha Motor Co Ltd | Cylinder head arrangement for a multi-valve internal combustion engine with an overhead camshaft |
JP2003193818A (en) * | 2001-12-21 | 2003-07-09 | Aichi Mach Ind Co Ltd | Oil supply structure to camshaft bearing part |
JP5078313B2 (en) * | 2006-10-17 | 2012-11-21 | 川崎重工業株式会社 | Motorcycle |
JP4723453B2 (en) * | 2006-10-17 | 2011-07-13 | 川崎重工業株式会社 | Engine and motorcycle |
JP6213200B2 (en) * | 2013-12-09 | 2017-10-18 | 三菱自動車工業株式会社 | Engine cam cap |
JP2017048707A (en) * | 2015-09-01 | 2017-03-09 | いすゞ自動車株式会社 | Positioning structure of cylinder head cover |
DE102019000489A1 (en) * | 2019-01-23 | 2020-07-23 | Deutz Aktiengesellschaft | Oil supply |
JP7322514B2 (en) * | 2019-05-28 | 2023-08-08 | マツダ株式会社 | cylinder head |
WO2024095432A1 (en) * | 2022-11-04 | 2024-05-10 | 日産自動車株式会社 | Cylinder head structure of internal combustion engine |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2552820A1 (en) * | 1983-10-04 | 1985-04-05 | Honda Motor Co Ltd | CYLINDER CYLINDER HEAD FOR INTERNAL COMBUSTION ENGINE OF THE DOUBLE CAMSHAFT IN THE HEAD |
EP0212981A2 (en) * | 1985-08-21 | 1987-03-04 | Honda Giken Kogyo Kabushiki Kaisha | Oil supply system for a valve operating mechanism in internal combustion engines |
US4709667A (en) * | 1985-05-14 | 1987-12-01 | Honda Giken Kogyo Kabushiki Kaisha | Oil supply device for valve operating system having hydraulic tappet in internal combustion engine |
GB2216187A (en) * | 1988-02-22 | 1989-10-04 | Nissan Motor | Oil return from a cylinder head for dohc i.c. engine with four valves per cylinder |
GB2224313A (en) * | 1988-10-29 | 1990-05-02 | Fuji Heavy Ind Ltd | Lubricating double overhead camshaft opposed cylinder i.c. engines |
EP0408080A2 (en) * | 1989-07-13 | 1991-01-16 | Yamaha Hatsudoki Kabushiki Kaisha | Valve and spring arrangement for engine |
EP0408079A1 (en) * | 1989-07-14 | 1991-01-16 | Yamaha Hatsudoki Kabushiki Kaisha | Valve actuating arrangement for engine |
EP0420139B1 (en) * | 1989-09-28 | 1996-02-14 | Mazda Motor Corporation | Multi-valve engine |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61261613A (en) * | 1985-05-15 | 1986-11-19 | Honda Motor Co Ltd | Oil feeder of tappet mechanism equipped with hydraulic tappet for multi-cylinder internal-combustion engine |
JPH0622092Y2 (en) * | 1987-04-29 | 1994-06-08 | スズキ株式会社 | Internal combustion engine oil passage |
DE3743854A1 (en) * | 1987-12-23 | 1989-07-06 | Michael Stirm | Four-valve control with upper supporting elements |
-
1989
- 1989-07-14 JP JP1181893A patent/JP2829866B2/en not_active Expired - Fee Related
-
1990
- 1990-07-13 EP EP19900113491 patent/EP0408081B1/en not_active Expired - Lifetime
- 1990-07-13 DE DE1990624117 patent/DE69024117T2/en not_active Expired - Fee Related
- 1990-07-13 EP EP95101503A patent/EP0654589B1/en not_active Expired - Lifetime
- 1990-07-13 DE DE1990631806 patent/DE69031806T2/en not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2552820A1 (en) * | 1983-10-04 | 1985-04-05 | Honda Motor Co Ltd | CYLINDER CYLINDER HEAD FOR INTERNAL COMBUSTION ENGINE OF THE DOUBLE CAMSHAFT IN THE HEAD |
US4709667A (en) * | 1985-05-14 | 1987-12-01 | Honda Giken Kogyo Kabushiki Kaisha | Oil supply device for valve operating system having hydraulic tappet in internal combustion engine |
EP0212981A2 (en) * | 1985-08-21 | 1987-03-04 | Honda Giken Kogyo Kabushiki Kaisha | Oil supply system for a valve operating mechanism in internal combustion engines |
GB2216187A (en) * | 1988-02-22 | 1989-10-04 | Nissan Motor | Oil return from a cylinder head for dohc i.c. engine with four valves per cylinder |
GB2224313A (en) * | 1988-10-29 | 1990-05-02 | Fuji Heavy Ind Ltd | Lubricating double overhead camshaft opposed cylinder i.c. engines |
EP0408080A2 (en) * | 1989-07-13 | 1991-01-16 | Yamaha Hatsudoki Kabushiki Kaisha | Valve and spring arrangement for engine |
EP0408079A1 (en) * | 1989-07-14 | 1991-01-16 | Yamaha Hatsudoki Kabushiki Kaisha | Valve actuating arrangement for engine |
EP0420139B1 (en) * | 1989-09-28 | 1996-02-14 | Mazda Motor Corporation | Multi-valve engine |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0854272A1 (en) * | 1997-01-21 | 1998-07-22 | Isuzu Motors Limited | A valve operating apparatus of DOHC |
EP0890713A3 (en) * | 1997-07-12 | 1999-03-31 | DEUTZ Aktiengesellschaft | Camshaft bearing frame |
EP1006272A3 (en) * | 1998-12-01 | 2003-01-29 | Honda Giken Kogyo Kabushiki Kaisha | Cylinder head structure in multi-cylinder engine |
US6513506B1 (en) | 1998-12-01 | 2003-02-04 | Honda Giken Kogyo Kabushiki Kaisha | Cylinder head structure in multi-cylinder engine |
US6672296B2 (en) | 1998-12-01 | 2004-01-06 | Honda Giken Kogyo Kabushiki Kaisha | Cylinder head structure in multi-cylinder engine |
EP1722090A3 (en) * | 1998-12-01 | 2009-11-04 | Honda Giken Kogyo Kabushiki Kaisha | Cylinder head structure in multi-cylinder engine |
CN109707526A (en) * | 2018-12-26 | 2019-05-03 | 郭严成 | A kind of automobile engine using new energy resources cylinder cap of positioning igniting |
CN109707526B (en) * | 2018-12-26 | 2021-12-14 | 濉溪泰高科技有限公司 | New energy automobile engine cylinder lid of location ignition |
Also Published As
Publication number | Publication date |
---|---|
DE69024117T2 (en) | 1996-05-09 |
EP0408081A1 (en) | 1991-01-16 |
JPH0347417A (en) | 1991-02-28 |
EP0408081B1 (en) | 1995-12-13 |
EP0654589A3 (en) | 1995-06-28 |
DE69024117D1 (en) | 1996-01-25 |
JP2829866B2 (en) | 1998-12-02 |
DE69031806T2 (en) | 1998-05-07 |
EP0654589B1 (en) | 1997-12-10 |
DE69031806D1 (en) | 1998-01-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5161495A (en) | Lubrication arrangement for engine | |
CA1328589C (en) | Oil supply system for a valve operating mechanism in internal combustion engines | |
US6289861B1 (en) | Control for variable valve timing | |
US5186129A (en) | Intermittent oiling system for an internal combustion engine camshaft and valve train | |
EP0654589B1 (en) | Cylinder head lubricating system of an internal combustion engine | |
US5016592A (en) | Cylinder head and valve train arrangement for multiple valve engine | |
US6467166B1 (en) | Method of forming a camshaft for an engine | |
USRE35382E (en) | Lubrication arrangement for engine | |
US5704330A (en) | Cylinder head arrangement for internal combustion engine | |
US4649874A (en) | Oil supply system for valves in an internal combustion engine | |
US5099812A (en) | Cylinder head for internal combustion engine | |
US5125374A (en) | Valve actuating arrangement for engine | |
US4649873A (en) | Oil return system for overhead cam engine | |
US5398649A (en) | S.O.H.C. five valve engine | |
US5121718A (en) | Valve and spring arrangement for engine | |
US5018497A (en) | Multiple valve internal combustion engine | |
US5522354A (en) | Valve mechanism for internal combustion engine | |
US4991549A (en) | Camshaft lubricating system for engine | |
EP0377829B2 (en) | Camshaft lubrication system for an internal-combustion engine | |
US6691658B2 (en) | Rotation prevention structure of a valve lifter for an internal combustion engine | |
EP0652356A1 (en) | Journal bearing oil diverter | |
EP0608557B1 (en) | Internal combustion engine | |
JP3133983B2 (en) | Lubrication system for 4-cycle engine | |
JP2528261Y2 (en) | Thrust bearing structure of camshaft | |
US6209507B1 (en) | Valve mechanism for internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 408081 Country of ref document: EP |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): DE FR GB |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): DE FR GB |
|
17P | Request for examination filed |
Effective date: 19951227 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
17Q | First examination report despatched |
Effective date: 19970217 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 408081 Country of ref document: EP |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REF | Corresponds to: |
Ref document number: 69031806 Country of ref document: DE Date of ref document: 19980122 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20010709 Year of fee payment: 12 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20010711 Year of fee payment: 12 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20010712 Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20020713 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20030201 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20020713 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20030331 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |